Bearing



Get. 1%, 1945. 1.. s. WILLIAMS 3 BE-ARING Filed Nov. 7, 1942 v s Sheets-Sheet 1 Lawrence .S W/W/ams INV ENTOR ATTORNEYS -0ct. 16,1945. L. s. WILLIAMS 2,387,202

BEARING Filed Nov. 7, 1942 s Sheets-Sheet 2 Lawrence 5. VV/W/ams INVENTOR.

U W I TTORN-EYS Oct. 16; 1945. y L. s. WILLIAMQS BEARING Filed Nov. 7, 1942 f 5 Sh eets-She et 3 Lawirehce 5. PV/W/ahs INVENTOR Patented Oct. 16, 1945 UNITED STAT i515 PATENT Q-FFICE BEARING Lawrence S. Williams, Toledo, Ohio, assignor to Toledo Scale Company, Toledo, Ohio, a corporation of New Jersey I Application November 7, 1942, Serial NO. 4645849- 9 Claims.

This invention relates to bearings for the pivotal mountingof oscillating members where the angular magnitude of the oscillations issubstantially less than the 360. I

In many types of scientific and highly accurate commercial equipmentit is necessary to mount oscillating members, such as levers, pendulums and indicators,- so they will be as friction-free as possible in their mountings and thus will not create errors in the equipment of which they are apart.- One method of mounting such members has been by the use of knife edge pivots and V block bearings; This type of mounting has a very low coefiic'ient of friction and has been satis'tactory except where the possibility of riding out" of the knife edges has existed.

When the force acting upon the oscillating member disturbs its center of gravity, or exerts a sidewis'e force on the" member, it'mayvery easily lift one or more of the knife edges out of the bearings inwhi'ch it rests. This will cause incorrect operation by introducing additional friction: and by causing shift (a change in the distances between pivots) and even may damage the knife edge or the bearing itself.

To eliminate the possibility of riding out, osciliating'members have been mounted in standard ball bearings, the outer race being-fastened to the stationary portion of the instrument and the balls carrying an. axle or shaft which su ports the oscillating member. Small as is the friction in a standard ball bearing it has still beenfound to be toov great in many instances and the beneficial result of the use ofball-bearings, thatis the preventionof: riding. out!" has been more than overcome by the increased friction resulting from the use of the ball bearings.

It is an. object of this invention to provide a bearing for mounting oscillatory members having, an angular magnitude of oscillation substantially less than 360".

It is afur'ther object of this invention to pro vi'de: a bearing fox-mounting oscillating members" which will prevent riding out 'oftl rememb'ers and yet will have a low coefiicienti of friction.

It isanother object of this invention to provide a ball bearing: having only twoballs for a su portin the oscillating member thereon. v

It isa still furtl ier object of this invention to provide a two-ball bearing for mounting oscillatirig members, the angular magnitude or" oscillation of which is'knoiv'n or can be estimated; and whieh' may be modified to provide thebest form mountedof construction for the particular magnitude of oscillation and degree of sensitivity desired.

It is-yetanotner object of this invention to rovide a ball bearing for mounting oscillating members" will dritfol the-aofi'ofi (if the aritifr'ictioii balls ineorporated'therein.

A further-object or this invention is to providea two hall bearing which will 4 automatically maintain the balls inspaced relation, thus eliminating friction caused by the balls rubbing to- More specific objects" and advantages are apparent from the dscti-ptioii, in Whichreference is had to the accompan ing drawings illustrating preferred forms of bearings embodying the invention. 7

In the drawings:

Fig. I is a View iii elevation, certain parts being shown in section and cert-ant pafts bfdkenaway; of a weighing scale eniployirl-g bearings embodying the invention.

Fig. II is a vertical sectional view; taken substantiahy from the position indicated by the liiie II-I]Z' of Fig. I'. v

Fig. III is an enlarged detailed view, taken stiltstant'i'ally' on the line lII1'-I'Iof Fig. II and mustr'atiiig a bearing embodying the invention.

Fig. IV is a view similar to III, but of another bearing embodying the invention incorporated the scale illustrated in Fig. I.

Fig. VIII is adiagram illustrating construction principles and the calculations involved therein of a bearing embodying the invention.

Fig. ix is a similar diagram illustrating other construction principles.

Fig. X'is still another diagram illustrating construction principles. v v

Fig; XI is a fragmentary view, in elevation, of the indicator of an even balance scale equipped with a bearing embodying a refined modification of the invention.

Fig. isa vertical sectionalview on an enl'arged scale, taken on the'line XII-XII of Fig. XI.

Fig. XIII is vertical sectional View taken substant'ia'lly on theline of Fig. XII.

seats of the fulcrum stands H by clamps l3.

Mounted in thebearings I2 is a main lever I 4 which extends horizontally above the base 10. A load receiver I5 is supported on a spider l6 which extends downwardly through an opening in the upper surface of a housing I! mounted on the base l0. Bearings l8 are mounted in the spider l6 and ride on load pivots I9 of the main lever I 4. An arm 20 of the spider l6 extends along within the housing [I and then upwardly intoan upper housing 2| where it is connectedto a bar 22 which is pivotally attached to a link 23 pivotally connected to the inner wall of the housing 2|. The arm 20, bar 22 and link 23 form a checking parallelogram for the load receiver IE to insure its vertical movement. A cone-point pivot 24 is mounted in the nose end of the lever l4 and rests in a stirrup 25 which is attached to the lower end of a vertically extending metallic ribbon 26. The upper end of the ribbon 26 overlies the arcuate face of, and is clamped to, a sector-like cam 21 which is an integral part of a load counterbalancing pendulum 28 pivotally mounted in bearings 29 supported in a bracket 30 attached to the housing 2!. An indicator 3| is attached to the pendulum 28 and sweeps over a fan-shaped chart 32 to indicate the weight of load placed upon the scale.

. Extending horizontally from the main lever I 4 (Fig. II) are two tapered shank pins 33, which serve astrunnions for the main lever I4 in cooperation with the bearings [2. Each of the pins 33 has a cylindrically-shaped portion which extends into a bearing l2 and on the end of which there is turned a shar point. Each bearing l2 (FigsII-and III) consists of an outer housing 34, in which are clamped side wall members 35 and 36, and an outer race3l. The members 35 and 36 are held in place in the housing 34 by the clamping action of a retaining nut 38 screwed into the housing 34. The retaining nut 38 also holds a thrust disk 39 against which bears the point on the end of the pin 33. A substantially C shaped spacer 49 is located in the space between the outer race 31 and the pivot pin 33. Two balls 4| and 42 are located in the-remaining-space between the outer race 31 and the pin 33 and are in contact with both the race and the pin, thus serving to support the pin 33 in the bearing l2.

In Fig. IV,- which illustrates the bearing 29, the construction shown is identical with that shown in Fig. III with the exception that the angular amplitude of oscillation of the pin which is fixed to the pendulum 28 is much larger than that of the pin 33 fixed to the main lever l4. Anouter housing 34a, has clamped therein an outer race 31a between the inner surface of which and a pin 33a there is located a substantially C shaped spacer 40a and two balls Ma and 42a.

In Fig. V a .hemispherically-shaped compass bowl 43 is supported by pins 44 (Fig. VI) which are held in bores 45,in the body of the bowl 43, y t s rews 46. The pins 44 pivot the bead 43 in bearings 41 which are fastened, by means of set screws 49, into a gimbal ring 48 surrounding the compass bowl 43. The two bearings 41 are diametrically opposed and thus pivotally support the compass bowl 43 for oscillation in one direction. 'A second set of bearings 59 are similarly fastened into the gimbal ring 48, their center lines being at an angle of from the center lines of the bearings 41. Pins 5|, which extend into the bearings 5!! as pivots, are clamped in vertical posts 52 which are fastened to the base of an outer housing 53.

The mounting for the compass bowl 43 is the standard gimbal mounting in which bearings embodying the invention replace knife edges or standard ball bearings. The bearings 41 are identical in construction with the bearings illustrated in Figures I11 and IV and comprise outer housings 54 in which are clamped, by means of a clamp nut 55, side wall members 56, an outer race '5'! and a thrust disk 58. Located in the space between the inner surface of the race 51 and the pin 44 are a spacer 59 and two balls 60 and 6!.

The rules and principles of construction of the bearings illustrated in Figs. III, IV and VII are shown in the diagrams of Figs. VIII, IX and X.

In constructing bearings embodying the invention the first requirement is that the sum of the diameters of the shaft and of the two balls must be equal to the inner diameter of the outer race and the shaft must be concentrically located with respect to the outer race. The relative size of the shaft and balls may vary, as shown by a comparison of the diameters of the shafts and balls in Figs. VIII and IX, as long as the conditions mentioned above are maintained. The force created by the load carried on the shaft is radially borne by the twoballs no matter what their relative size to the shaft as long as they do not get diametrically opposed on opposite sides of the shaft. If the two balls are permitted to get degrees apart, they will no longer support the shaft, which will fall between the. balls to the bottom of the race. This, then is the second principle governing the construction of the bearings herein disclosed. The spacer or other means located in the space between the inner wall of the race and the shaft, must prevent the balls from reaching such a diametrically opposed position.

Although the shaft will be perfectly supported )2] the balls no matter how far apart they'are permitted'to get, as long as the angular relation between their centers is less than 180 degrees, the'further apart they are permitted to get the greater will be the load carried by each individual ball. In Fig. VIII, the lines OF and 0G are drawn through the center of the shaft 0 and the centers J and C of the balls X and Y respectively. If the balls are so positioned that the angle FOG is bisected by a vertically drawn line OH, tangent to both of the balls, which may arbitrarily be allowed to represent the number of pounds or ounces or grams of force acting on the shaft, then the force acting on each ball may be calculated as follows:

A force parallelogram FOGI-I is constructed in which the lines OF and 0G represent the components of the force represented by the line OH, which act on each of the balls. The angle FOG being bisected by the line OI-I results in the line FG, connecting the points F and G, being perpendicular to the line OH at its center point. Therefore, the line OI represents one-half as much force as the line O H-and the .angle OIG is raasneoe 90".. With these two facts the length of the lines 'QF and 06;, which :represent the number 10f grams-force acting on :each of the balls, :is:

With this formula in mind, referring to .Fig. IX, it can be seen that the angle IO'G has a muohigreater number of degrees than the angle lC} in Fig. and therefore, by applying the formula, if .071 equals OI, it is found that the length of the :Line -O-F' or 0 6' (the force acting on the individual balls) is much greater than the length of the line :OF or 06.

It is therefore very desirable that the balls be kept as close together :as possible at all times. The angular relation of .the faces of the spacer member, inmumber of degrees, is ,a function of the sizeof the balls-and the shaft and the number of-degrees through which the shaftcscillates. 3

A=FOG=the angulardisplacement of one ofthe balls, in degrees I a=the angle of oscillation of the shaft, in degrees T=OB=the radius of the shaft, in units of .measurement I R=BC=EC=the radius .of the halls, in units of measurement M=the angular relation of the faces of the spacer, in degrees, then,

' B M=A+A+ 230120 Or, in general terms:

Applying these formulae to the bearing illustrated diagrammatically, in Fig. 'VIII, reveals the following further facts:

In Fig. VIII, let,

a=45 degrees 1:1 unit 'of measurement R=2 units of measurement M 1.88% ('approx.)

Force on each ball= rjtherefore, the angular .irelation betweellfthe faces of *a hearing having :balls 2 times the diameter of :a ,shaft which turns through 45, :should be 188 9..

However, a bearing constructed with such large balls, with reference to the size of the shaft, has some disadvantages. Among these are the large size of the outer race whichis required :and the possibility that the inertia of the :ballsmay .be difiicult 'to overcome with the shaft and that the shaft will slide on the surfaces of the balls. It may, therefore, be desirable to consider the opposite extreme, as illustrated in Eigs. .IX and X Where the diameter of the shaft is four times the diameter \of the halls.

Considering Fig. IX first, it has already been mentioned that .a design sue-has this would "not be practical because of the fact that the balls would be --perrnitted to get so farapart inthe race that-the force [on each ball would be very large. For purposes of illustration the angular relation "between the faces of the spacer, M, has "been made such that lines drawn :between the center 'of the shaft and the centers of the balls intersect at an angle of If we let:

I ='l1% plus A'=-23 and, therefor since the lines eonnecting the center :of the balls meet at 175 This will maintain support of :the shaft, bythe balls, but, .if the load'on the shaft is 10 units of weight then:

f Load -on each ba1l-= 5 -114.62 (as .compared .to 7.13 forthe ratios illustrated in Fig. VII) which is .a prohibitive force since it would create a great amount of friction.

It ,is for this "reason, :as explained generally above, that the spacer should be so designed that itoccupiesall but the space needed by the twoballs to permit-them to make a partial revolution around .the shaft underdmpetuspf the partial rotation of the shaft.

Referring now to Fig. X, thebearing diagrammatically-illustratedihere, has the same respective shaft and ball diameters as that illustratedin Fig. IX,.but has the spacer .constructedto maintain the conditions .just described with relation to the space between the balls.

A=23, as calculated above "Then:

'M=,64 The maximumiforce.onieach ball, even if the balls become separated as far as possible so that they touch the spacerlas in Fig. IX) with a 4:1"v

, 5 5 Force on It is to be noted, however, that in the bearing of Fig. X, the balls would be brought back together upon completion of the first oscillation of the shaft, due to the action of the spacer and that in Fig. IX, they would not. (Assumingthe same angle of oscillation of the shaft in both instances.)

Construction of this kind, however, presents a further practical difficulty which is the provision of small enough balls to permit'the extreme ratios between size of shaft a d of balls to give such excellent'low forces acting on each ball. In instruments of the type for which the bearings embodying the invention are'primarily designed, the shafts are often as small as of an inch in diameter and, thus balls would have to be 34 of an inch. in diameter, which would not be practical. For these many reasons, it has been found that the most practical ratios between the shafts and balls are those in which the'lines from the center of the shaft through the centers of the balls, when adjacent, meet at angles of from 50 to 90; or a range in ratios of the radius of the shaft to the radii of the balls of from approximately 1:2 to 3:2. The spacers, of course, should be constructed in accordance with Fig. VIII (Fig. IX illustrates an undesirable situation).

In Fig. XI there is illustrated a scale indicator 62 which cooperates with a chart 63 having a centrally located zero indicium 64 to indicate a condition of balancein a scale of the even-armed or over and under type. (Mechanism connecting the indicator to the weighting scale, since it is not partof the instant invention, is not shown but it maybe any standard device.) The indicator 62 is mounted on a shaft 65 which extends into the interior of a pair of ball bearing housings 66, one of which is mounted on each side of the plane of movementof the indicator 62. Each of the ball bearing housings 56 is held in place on a frame member 61 by means of a C shaped clamp 68. i

The ball bearing housing 66 is substantially cup-shaped, having an inside thread into which is threaded a disk-shaped retainer 69 serving to hold in place a thrust plate HI, an end plate H, an annular member 12, and two balls 13 and 14. The annular member 12 has a notch in its periphery in which is engaged a cone point set screw 16 for correctly positioning the annular I member relative to the housing 66 through which the set screw I6 is threaded. The center hole of the annular member 12 serves asthe outside race for the two balls 13 and 14 supporting the indicator shaft 65. Three notches TI, 18 and '19 are cut in the annular'mernber I2. Three very carefully positioned holes 80 are drilled through the annular member 12 extending radially from the center of the member 12 into the notches TI, 18 and 79.. Wedge-pointed The holes through which the pins are inserted, and the pins themselves, must be very carefully located and constructed because they serve as the limiting means for the oscillations of the two balls 73 and 14 caused by the oscillations of the shaft 65 and the indicator 62. The end stops 8! and 82 serve the same purpose as the O shaped stop members 40 in the embodiments of the invention described in Figs. I through X, i. e., to limit the outward movement of the balls. They must be so positioned and constructed that when one of the balls is in contact with one of the outer stops, and the indicator is at one of the extreme points of oscillation, a line drawn through the center of theshaft 65 tangential to the outer edge of the ball in contact will mark the side of the maximum angle through which the ball is movable under impetus of the oscillation of the shaft 65. In other words, upon the oscillation of the shaft 65 and the indicator 62, through the predetermined angle, each of the balls 13 and M revolves through a specified angle around v The center stop 83 has been provided, in this more sensitive embodiment of the invention, to cooperate with the outer stops in maintaining a definite clearance between the adjacent surfaces of the balls 13 and 74. If these surfaces are permitted to come in contact, as would occur in the embodiment of the invention explained in Fig. VIII, since the contacting surfaces are moving in opposite directions at all times, friction is created which appreciably detracts from the accuracy of a highly sensitive scale. The center stop 83 however does not prevent the two balls 13 and M from coming into contact. They can still do this if the scale is jarred so that one or both of them is moved relative to the race or the center shaft. But, the center stop and the end stops limit the travel of the balls under the predetermined oscil lation of the indicator. If, for example, the ball 14 is jolted downwardly and comes into contact with the ball 13, the first oscillation of the indicator in a clockwise direction will correct this condition. When the indicator is rotated in a clockwise direction, the balls 13 and M revolve around the shaft 65 in a clockwise direction and the ball 14 strikes the corner 85 of the center stop 83 before the indicator is swung to the limit of its oscillation. The ball 14, therefore, since it can move no further, rotates in position sliding on the race formed by the inner surface of the annular member 12 and the shoulder 85 until the indicator reaches the limit of its oscillation and the ball 13 comes into contact with the left-hand stop 8|. At this point the two balls once again are properly spaced and will remain so spaced until the scale inadvertently receives another blow or jar after which they can be restored to their correct spacing by a single oscillation of the indicator.

Contact between the ballsdoes not destroy the accuracy of the scale other than momentarily.

The first oscillation thereafter restores the balls to their proper spaced relationship. This first oscillation, of course, occurs as soon as an article to Joe -weighed is placed on oneof the scale platters. a A bearing of thismore accurate type is constructed accordingto principles similar to those employed in they construction of the-simpler form. In Fig. XIV: R=radius of the ball; r=radius of the :shaft; a the oscillation of the shaft in degrees; and b=one-half of the clearance .to be maintained between the balls. The value .b is purel-y'arbitrary and mm terms of linear (not angular distance. --Itshould be :as small .as .practicablyicanbe-maintained. r

y In Fig. XIV there has been constructed a. center line-which serves'as .a locating line from which the positions of the twoendstops and the center stop may Jae-calculated. This center line is equidistantly positioned between the surfaces .ofthe two balls when the shaft is centrally located and the indicator-standsat zero. In Fig. KW, each of-the balls is shown inthree important positions, the left-hand ball being used for purposes of calculation andbeing shown in its three positions, designated X, Y and Z, the Xposition being shown'in dash lines at the limit-of outward travel, the Z position being shown in .dotted lines at the limit of inward travel and the Y position being shown in solid lines equidistantly :between these two- (the position of the ball-when the shaft 65 and-indicator 62 are located centrally between their extrernes of oscillation). The three corresponding positions of the right-hand ball-are shown in lines corresponding to those used to illustrate thethreepositions of the left-hand ball. The above mentionedcenter line is indicated by the line CA and its vertical extension, drawn fromth'e'center C of the shaft through a point equidistant between the two balls when they are at their central (solid line) position. a is the angle between two lines CD and CE drawn through the point C tangential to opposite sides of the left-hand ball .in its :outside dash-line position. (d=the angular displace ment of the ball in the race.) c is the angle subtended' bythe center .1ine=CA and aline CB drawn from the-centerof the shafttothecenter of the left han'd ball in its central" (solid line) position. -e may thenbe calculated according to equation number (2) in the above calculations where:

x sine angle BCA=g g .or .sine 21: d (the angular displacement of the'ball) is calculated according to Equation'NuniberfZ (as illustrated in Fig.'VIII) v.

. E R l-r The angle f'is equalto "the'travel in degrees of the'center point 'B'of the left-handball between itsrnaxirnum points F and G and is calculated'by the equation:

sine

, .The nextline tobe. located is the line'CI-I which passes through the center of the shaft and-is tangential to the innermost surface of the ball in :its innermost .(dotted line) position :2. *The angular relationship between this .line and the I v =.y f Theparticularform.of the end and center stops is not essential to the invention, itbeing necessary only that they are constructed and placed to limit the travel of each of the balls to the angle g in Fig. XIV. This angle g varies according to the oscillation tor the shaft and, of :cour'se according to the ratios between the radii of the shaft and the balls, and may vary because "of a-change in the arbitrary clearance distance 2b which is desired to be maintained between-the balls.

If an outer stop of the type disclosed in'Figures VIII, IX and X, i. e., a C shaped =spacer, is used in the bearing of Fig. XIV, 'the -faces-of the spacer are designed to lie on the line CD and-on the corresponding *line'on the .opposite side of the bearing. I I

If, however, the wedge-pointed '-pin s of Figs. XII and XIII are usedlthey are shown inposition in Fig. XIV) :the lines CD and CH need not be calculated, It is only necessary to locate the points "F and G and to construct the circles Y and Z. The points of contact between the stops and the balls can lie anywhere on the r espective circles representing the balls in the positions of contact. (For example, the point :84 lies-on-the circle Z, iin'Fig. XIV); I .Although the particular shape of-the stops is not essential to the bearing of Fig. XIV, the wedge-pointed:pins- -disclosed are particularly desirable because a hearing so equipped can be adapted for use :with oscillating members having difierlentangles of oscillation merely by inserting the pin into .therace farther or less far to give the balls a less-.or greater free space for oscillation. I

.It has been found that bearings constructed according'zto this nner :more accurate modification -.of the invention w ith the above described clearance :maintaining feature only have approximately Jone-tenth as much friction as bearings constructed in accordance with the si'mplende- Sign disclosed. 1

.The embodiments of I the invention that have been disclosed may be modified :to .meet various requirements.

' :Having1 described the invention, I claim:

v1. .Anantifri'ction bearing .for mounting. trunnions of .an oscillating member having an angle ofloscillationbf.substantiallyless:than1360 comprising :an outer irace concentric with respect to the;tr.unnions,:-two supporting ballslocatedthereimandsstopszattachedito said race-including:a-stop betweenssaidballslforudefining-the limits of :movem'entlbffeach. ofsaidiballs'.

2. An antifriction shaft bearing comprising two supporting balls, a race in which said balls ro tate, said race being concentric with respect to the shaft, and. fixed stops inserted through said race for defining the limits of travel of each of said balls independently of the other, said stops 6 assi ts havingopposing faces between which said balls travel. Y i r 3. Mounting means for an oscillating member comprising trunnions extending coaxially from opposite sides of said member and bearings for said trunnions, each of said bearings comprising an outer race, a pair of antifriction support balls lying in said race and supporting said trunnion, spacing means fixed in said race including a stop inserted between saidballs and fixed in said race for limiting the rolling. movement of said balls, thespace allowed for said balls andtheir movement being defined by the angle ,M subtended by two lines drawnthrough the center of said shaft, each tangential to the leading surface of the leading ball at the two'extremes of movement of said balls, being calculated by the equation:

2R"+"2% whereAequals the angle, subtended bytwo lines tangential to opposite sides ofone of said balls and passing through the center of said shaft; R. equals the radius ,ofone of said balls, 1' equals the radius of said shaft, 2b equals the space between theballs and a equals the angle of ,oscillationfof said shaft. J; 1, l.

4 antif riction mounting for angoscillatory member having a; given angle of oscillationcome prisin a pair of pin-like trurmions extending co.- axially from oppositesides of said membenand a bearing into which eacher said trunnions .extends, each of said bearings comprising; an outer rac e,;a pair of ballspsupportedin .saidrace; and supporting that one;of; said, trunnions extending therein concentrically with said raceland spacers fixedinsaid raceincluding .a spacer fixed to. said race: between the balls to prevent either of, said ballsfrom rolling around said. trunnion further than that distance said ball ismoved by the oscillation of said member and said: trunnion. l

;;; 5. i tntif riction monntingmeans for: an oscillatory member having a; given angle of oscillation on each side of a center position .comprising, a pair-of pin-like trunnions extending coaxially in opposite -directions'from,said. member, and a bearing for each of said trunnions, each of said in-responseto thegiven oscillation of said mem her and said trunnion. V

I '7. Mounting means for an oscillatory member having a given'angle of oscillation on each side .of a center position comprising, a pair of pin-like trunnions extending 'rcoaxially in opposite, directions from said member, and a bearing for each of said trunnions, each of said bearings comprising an outer-race, a pair of balls located in said race and-supporting said trunnion concentrically with said race, the adjacent surfaces of said balls being spaced a predetermined distance apart by a fixed, stop in said raceon each side or each of each balls, said stops being so located as to be contacted by the leading surfaces of said balls when said balls have reachedthe limits of their rolling travel around said trunnion in response to oscillationsof said member and said trunnionto bearings comprising an outer race, a .pair of balls located in said raceand supporting said trunnion concentrically with said race, the adjacent sure faces ofsaidiballs being spaceda predetermined distanceflpartbyimeans-fixed in.said race for keepingsaid balls from rolling around said trunnion a distance greater, than .the distance said balls roll in response to'the. given oscillation of said member. andisaidtrunnione I. l l 6. Mounting means for an oscillatorymember having a given angle .of oscillationon each side of a-center position comprising, a paireof pin-like trunnions extending coaxially in opposite directions from .said'member, and a bearing for each of said trunnions,..each .of said bearings comprising an outer race, a pair. of balls located in said race and supportingsaidtrunnion concentrically with said .racathe adjacent surfaces of said balls being spaced a predetermined distance apart by fixed stops which prevent either of said balls from rollingaround said trunnion in either'direction a distance greater than the distance said ball rolls the limits of such given angle of oscillation, that one oisaid stops located between saidballs being contacted alternately by said balls when said member is at opposite extremes of such given angle of oscillation.

8. Mounting means for an oscillatory member having a given angle of oscillation on each side of a center position comprising, a pair of pin-like trunnions extending coaxially in opposite directions from said member, and a bearing for each of said trunnions, each of said bearings comprising an outer race, a pair of balls located in said race and supporting said trunnion concentrically with said race, the adjacent surfaces of said balls 7 being spaced a predetermined distance apart by a stop fixed in said race on each side of each of said balls, said stops being so located as to be contacted by the leading surfaces of said balls when said balls have reached the limits of their rolling travel around said trunnion in response to oscillations of said member and said trunnion to the limits of such given angle of oscillation, that one of said stops located between said balls being contacted alternately by said balls when said member is at opposite extremes of such givenangle of oscillation, the angular distance i between the center of one of said balls when in com tact with one of said stops and the center of said ball when in contact with another of said stops being when r equals the radius of said trunnion, R

equals the radius of either of said balls and a equals the angle between the limits of oscillation of said member and said trunnion.

9. An antifriction bearing for supporting trunnions of an oscillatory rnember which has a predetermined angle of oscillation, comprising an outer race concentric with respect to the axis of said trunnions, two supporting balls located therein, and means fixed in said race for defining the movement of each of said balls, said means being so spaced with respect to said balls and said race that said balls contact said means when said oscillatory member is at the limits of its travel and that said balls are independent of said means when said oscillatory member is intermediate its limits of travel.

LAWRENCE S. WILLIAMS. 

